WO2017141538A1 - Joint fileté pour conduite de puits de pétrole - Google Patents

Joint fileté pour conduite de puits de pétrole Download PDF

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Publication number
WO2017141538A1
WO2017141538A1 PCT/JP2016/087462 JP2016087462W WO2017141538A1 WO 2017141538 A1 WO2017141538 A1 WO 2017141538A1 JP 2016087462 W JP2016087462 W JP 2016087462W WO 2017141538 A1 WO2017141538 A1 WO 2017141538A1
Authority
WO
WIPO (PCT)
Prior art keywords
pin
seal
inch
box
nose
Prior art date
Application number
PCT/JP2016/087462
Other languages
English (en)
Japanese (ja)
Inventor
孝将 川井
太郎 金山
吉川　正樹
関　春彦
植田　正輝
順 高野
毅 米山
Original Assignee
Ｊｆｅスチール株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to CA3013300A priority Critical patent/CA3013300C/fr
Application filed by Ｊｆｅスチール株式会社 filed Critical Ｊｆｅスチール株式会社
Priority to MYPI2018702771A priority patent/MY189310A/en
Priority to US16/077,912 priority patent/US10900595B2/en
Priority to JP2017518364A priority patent/JP6187724B1/ja
Priority to AU2016393093A priority patent/AU2016393093B2/en
Priority to UAA201808799A priority patent/UA120020C2/uk
Priority to BR112018016593-0A priority patent/BR112018016593B1/pt
Priority to MX2018009994A priority patent/MX2018009994A/es
Priority to ES16890675T priority patent/ES2815848T3/es
Priority to RU2018129939A priority patent/RU2692177C1/ru
Priority to EP16890675.8A priority patent/EP3418617B1/fr
Publication of WO2017141538A1 publication Critical patent/WO2017141538A1/fr
Priority to SA518392131A priority patent/SA518392131B1/ar

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
    • F16L15/04—Screw-threaded joints; Forms of screw-threads for such joints with additional sealings

Definitions

  • the present invention relates to a threaded joint for oil well pipes generally used for exploration and production of oil wells and gas wells, and more particularly to a threaded joint for oil well pipes suitable for tubing applications.
  • Threaded joints are widely used to connect steel pipes used in oil industry equipment such as oil well pipes.
  • the wells for crude oil and natural gas have been deepened, and the number of vertical wells, horizontal wells, inclined wells, etc. has increased, and the drilling and production environment has become severe.
  • the demand for screw joints such as compression resistance, bending resistance, and external pressure seal performance (external pressure resistance) has diversified due to the increased development of wells in poor environments such as the ocean and polar regions.
  • standard threaded joints defined in API (American Petroleum Institute) standards are typically used to connect steel pipes used for oil and gas exploration and production.
  • premium joints due to the diversification of required performance, cases using high-performance special threaded joints called premium joints are increasing, and the demands on the performance are also increasing.
  • the premium joint is usually a joint provided with a taper screw, a seal portion (specifically, a metal touch seal portion), and a shoulder portion (specifically, a torque shoulder portion), and a male screw member (hereinafter referred to as a pin) formed on a pipe end portion. And a female screw member (hereinafter referred to as a box) that connects to one pin and couples the two pins.
  • the taper screw is important for firmly fixing the joint, and the seal part is formed by metal contact between the box and the pin, and plays a role of ensuring airtightness.
  • the shoulder part is used as a stopper during tightening of the joint. It becomes the shoulder side that plays the role.
  • Tubing that draws up production fluid (crude oil, natural gas, etc.) in the well design has a small outer diameter, and tends to be thinned to increase the cross-sectional area of the inner diameter through which the fluid passes in order to improve productivity.
  • the external pressure uses the value calculated based on the formula specified in API-5C3.
  • WT wall thickness
  • OD outer diameter
  • An object of the present invention is to provide a threaded joint for an oil well pipe that is suppressed and has sufficient airtightness (sufficient external pressure sealability) when an external pressure is applied.
  • a screw joint for an oil well pipe comprising: a female screw part that fits into the male screw part of the pin; and a box having a portion that faces the nose part,
  • the shoulder part located at the tip of the nose part of the pin is in contact with the shoulder part of the opposing box in the axial direction,
  • the outer surface of the nose of the pin is a convex curved surface
  • the inner surface of the opposing box is a tapered surface with an inclination angle of ⁇ with respect to the axial direction
  • Both the outer surface of the nose portion of the pin and the inner surface of the box have a structure that seals the fluid by metal contact in the radial direction when the joint is tightened,
  • the seal point is defined as the axial position where the radial overlap between the seal portions is maximized when the axial sectional views of both the pin and the box are overlapped
  • BRIEF DESCRIPTION OF THE DRAWINGS It is typical explanatory drawing which shows the premium joint for oil well pipes of the related technology of the threaded joint for oil well pipes of this invention, and is the schematic of a nose part.
  • BRIEF DESCRIPTION OF THE DRAWINGS It is typical explanatory drawing which shows the premium joint for oil well pipes of the related technique of the threaded joint for oil well pipes of this invention, and is the schematic of a thread part.
  • BRIEF DESCRIPTION OF THE DRAWINGS It is typical explanatory drawing which shows the premium joint for oil well pipes of the related technique of the threaded joint for oil well pipes of this invention, and is the schematic of the whole joint part. It is the figure which entered a part of parameter used by this invention in the schematic diagram of a radial seal type threaded joint.
  • FIGS. 1 to 3 are schematic explanatory views showing premium joints for oil well pipes according to the related art of thread joints for oil well pipes according to the present invention, which are longitudinal sectional views of thread joints of circular pipes (the pipe axis extends within the cross section). Existing sectional view).
  • the threaded joint 100 includes a pin 3 and a box 2 corresponding thereto.
  • the pin 3 has a male screw portion 7 on the outer surface thereof and a nose portion (also referred to as a pin nose) 8 which is a non-threaded length portion provided adjacent to the male screw portion 7 on the tip end side of the pin 3.
  • the nose portion 8 has a seal portion (specifically, a metal touch seal portion) 11 on its outer peripheral surface and a shoulder portion 12 on its end surface.
  • the box 2 has a female screw part 5, a seal part 13, a part that can be screwed or brought into contact with the inner thread part 7, the seal part 11, and the shoulder part 12 of the pin 3, respectively, on the inner surface thereof.
  • the pin 3 has a seal portion 11 at the tip, and a desired sealing performance can be realized by applying an appropriate tightening torque. Since the tightening torque is affected by lubrication conditions, surface properties, etc., as a design that does not depend greatly on these, a radial seal method with a relatively strong radial component of the seal contact pressure (hereinafter referred to as a radial seal type) There is.
  • the radial seal type is the same as the screw joint of the type having the seal part at the tip of the pin in that it has the seal part at a site different from the shoulder part, but when an axial tensile load is applied. There is an advantage that the seal contact pressure is difficult to reduce.
  • ⁇ is a load flank angle, and is defined by an angle formed by the load flank surface 9 of the threaded portion and the tube axis orthogonal surface.
  • the screw gap 15 is the distance between the pin side and the box side surface of the stubbing flank surface 10 of the screw when the pin and the load flank surface of the box are in contact with each other (the surface distance at the center position in the thread height direction). ).
  • FIG. 4 is a diagram in which some parameters used in the present invention are entered in a schematic diagram of a radial seal type threaded joint. 4, the same or corresponding parts as in FIGS. 1 to 3 are denoted by the same reference numerals, and description thereof is omitted.
  • This radial seal type threaded joint includes a pin 3 having an outer diameter (D1 described later) of 114.3 mm or less in which a nose portion is connected to the tip of the male screw portion, a female screw portion fitted to the male screw portion of the pin 3, and the nose portion 8 And a box 2 having a portion opposite to each other.
  • the shoulder portion 12 located at the tip of the nose portion 8 of the pin 3 abuts against the shoulder portion 14 of the box 2 in the axial direction.
  • the outer surface of the nose portion 8 of the pin 3 is a convex curved surface
  • the inner surface of the opposing box 2 is a tapered surface whose inclination angle (taper angle) is ⁇ with respect to the axial direction.
  • the pin-side seal portion 11 and the box-side seal portion 13 are structured such that both the outer surface of the nose portion 8 of the pin 3 and the inner surface of the box 2 seal the fluid by metal contact in the radial direction when the joint is tightened. Have.
  • the present invention can be applied to a joint having a pin outer diameter of 114.3 mm or less. It can also be applied to joints with a pin outer diameter of 114.3mm, which is the casing size described in API 5CT, but when the pin outer diameter exceeds 114.3mm, the following formulas 1 and 2 are satisfied, and Ls / Ln Even if it is not designed to fall within the scope of the present invention, it is possible to achieve both external pressure seal resistance and galling resistance. On the other hand, even if the outer diameter of the pin is 114.3 mm or less, it is designed so that the following formulas 1 and 2 are satisfied and Ls / Ln is within the scope of the present invention, so that it is resistant to external pressure and galling. It is possible to realize both sex.
  • Ds1 is a diameter (inch) indicating the upper end (outer diameter side end) position of the shoulder contact surface
  • Ds0 is a diameter (inch) indicating the lower end (inner diameter side) position of the shoulder contact surface.
  • the outer diameter D1 (inch) and inner diameter D0 (inch) of the unprocessed portion of the pin 3 are not shown in FIG.
  • the shoulder contact surface refers to a surface on which the shoulder portion 12 and the shoulder 14 abut.
  • the unprocessed portion of the pin 3 is a region where the male screw portion 7 on the rear end side does not exist when the shoulder portion 12 is the front end side in the pin 3, and the outer diameter and inner diameter are constant in the tube axis direction. Refers to the tube area.
  • ⁇ is the taper angle (°) of the seal portion 13 of the box 2.
  • Dn is the outer diameter (inches) of the nose portion of the pin 3. That is, Dn (inch) is the diameter of the pin 3 at the connection site between the nose portion 8 and the male screw portion 7.
  • Dsp is the outer diameter (inches) of the pin 3 at the seal point position.
  • ⁇ is a seal interference amount (inch).
  • This seal interference amount ⁇ is the overlap of the seal portion per diameter at the seal point position of the seal portion 20, which is a region formed by overlapping the seal portion 11 on the pin side and the seal portion 13 on the box side.
  • Lt is the end position index of the seal taper portion of the box 2 (expressed in the axial length from the pin tip) (inches).
  • Ls is a seal point position index (expressed as an axial length from the tip of the pin) (inches).
  • Ln is the length (inches) of the nose portion.
  • the seal point is the cross-sectional view of both the pin 3 and the box 2 in the axial direction when the shoulder portions (shoulder portion 12 and shoulder portion 14) are overlapped with each other (the seal portion 11 and the seal portion). This is the axial position where the overlap margin in the radial direction of the part 13) is maximum.
  • Ls / Ln is 0.3 or more.
  • Ls / Ln is 0.5 or less.
  • the nose length Ln is preferably 0.2 "(0.2 inch, 5.08 mm) or more.
  • the nose portion length Ln is preferably 1 ′′ (25.4 mm) or less, since it is difficult to satisfy the following formula 1 if the length is too long, and this is disadvantageous in terms of a decrease in sealing performance accompanying plastic deformation of the nose portion.
  • the cross-sectional area ratio of the shoulder portion means the ratio of the area of the orthogonal projection image of the contact surface of the shoulder portion to the axial orthogonal surface with respect to the axial orthogonal cross-sectional area of the unmachined portion of the pin. It is calculated by the formula on the left side of.
  • Ds1 2 -Ds0 2 Diameter (inches) representing the upper end position of the surface per shoulder
  • Ds0 Diameter (inches) representing the lower end position of the surface per shoulder
  • D1 Outer diameter of pin unprocessed part (inch)
  • D0 inner diameter (inch) of the unprocessed portion of the pin.
  • connection portion between the seal portion and the screw portion which is a portion connecting the seal portion and the screw portion. If the level difference between the seal part and the screw part becomes large due to the extreme design, contact at the joint part between the seal part and the screw part will occur at the beginning of the tightening process, and a large surface pressure will be generated, causing the Cause.
  • the present inventors have designed the above parameters so as to satisfy Equation 1 and Equation 2 below, while suppressing plastic deformation of the nose portion, It has been found that goling due to contact during tightening of the threaded portion to the connecting portion can be prevented.
  • Mathematical formula on the left side of Formula 1 means “shoulder cross-sectional area ratio”. By setting this value to 0.30 or more, plastic deformation of the nose portion can be effectively suppressed. Note that if the left side value of Equation 1 becomes excessive, Equation 2 will not hold, so the practical maximum value of the left side value of Equation 1 will be 0.5.
  • Expression 2 means an expression that represents a condition that ⁇ should satisfy so that the pin and the box do not interfere with each other at the end position of the seal taper portion of the box (position where the position index is Lt).
  • the thread used in the process of deriving Expressions 1 and 2 has 4 to 8 threads per shaft length of 1 ′′, and the load flank angle ⁇ and thread gap 15 (see FIG. 2)
  • the numerical ranges are ⁇ : -10 ° to 5 °, screw gap: 0.025mm to 0.200mm, and the unprocessed pin thickness (pin tube thickness) is 0.1 "to 1.0".
  • the effect of the present invention can be obtained by setting the threaded joint within the numerical range used in the derivation process of the above formulas 1 and 2 as the application target of the present invention.
  • examples of the steel type of the oil well pipe to which the threaded joint according to the present invention is applied include various steel types described in API-5CT.
  • a plurality of threaded joints for oil well pipes having boxes corresponding to these were prepared.
  • Each oil well pipe threaded joint has the specifications shown in Tables 1 and 2 when it is tightened with low torque (3500 ft ⁇ lb).
  • Each oil well pipe threaded joint was subjected to an airtightness test based on ISO13679: 2002.
  • the pin thread was 5 threads per 1 ”shaft length, the load flank angle ⁇ was ⁇ 5 °, and the screw gap 15 was 0.10 mm.
  • Table 3 shows the test results. As shown in Table 3, each of the inventive examples passed the airtightness test based on ISO13679: 2002, can be tightened without goling, suppresses plastic deformation, and has sufficient airtightness. It is clear.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Non-Disconnectible Joints And Screw-Threaded Joints (AREA)
  • Earth Drilling (AREA)
  • Lubricants (AREA)

Abstract

L'invention concerne un joint fileté destiné à des conduites de puits de pétrole, lequel présente une étanchéité à l'air suffisante (propriétés suffisantes d'étanchéité de résistance à la pression externe) sous une pression externe en conséquence de la suppression de déformation permanente d'une partie de nez du joint fileté et dans lequel un écorchage ne se produit pas lorsque le joint fileté est serré dans un essai d'étanchéité à l'air fondé sur la norme ISO13679:2002, même si le joint est destiné à un tubage présentant une faible épaisseur. Les paramètres comprenant les dimensions, aux positions d'un point d'étanchéité et d'une partie d'épaulement, de ce joint fileté satisfont l'expression 1 et l'expression 2, et Ls/Ln est défini de 0,2 à 0,6. (Ds12-Ds02)/(D12-D02)≥0,30 ... (expression 1) tanθ>(ΔD+δ)/{2(Lt-Ls)} ... (expression 2)
PCT/JP2016/087462 2016-02-19 2016-12-16 Joint fileté pour conduite de puits de pétrole WO2017141538A1 (fr)

Priority Applications (12)

Application Number Priority Date Filing Date Title
UAA201808799A UA120020C2 (uk) 2016-02-19 2016-12-16 Різьбове з'єднання насосно-компресорних труб для нафтових свердловин
MYPI2018702771A MY189310A (en) 2016-02-19 2016-12-16 Threaded joint for oil well tubing
US16/077,912 US10900595B2 (en) 2016-02-19 2016-12-16 Threaded joint for oil well tubing
JP2017518364A JP6187724B1 (ja) 2016-02-19 2016-12-16 油井管用ねじ継手
AU2016393093A AU2016393093B2 (en) 2016-02-19 2016-12-16 Threaded joint for oil well tubing
CA3013300A CA3013300C (fr) 2016-02-19 2016-12-16 Joint filete pour conduite de puits de petrole
BR112018016593-0A BR112018016593B1 (pt) 2016-02-19 2016-12-16 Junta rosqueada para tubulação de poço de petróleo
RU2018129939A RU2692177C1 (ru) 2016-02-19 2016-12-16 Резьбовое соединение насосно-компрессорных труб для нефтяных скважин
ES16890675T ES2815848T3 (es) 2016-02-19 2016-12-16 Unión roscada para tuberías de pozos petrolíferos
MX2018009994A MX2018009994A (es) 2016-02-19 2016-12-16 Junta roscada para tuberia de pozo petrolero.
EP16890675.8A EP3418617B1 (fr) 2016-02-19 2016-12-16 Joint fileté pour conduite de puits de pétrole
SA518392131A SA518392131B1 (ar) 2016-02-19 2018-08-01 مسنن مفصل لأنابيب حقل النفط

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-029653 2016-02-19
JP2016029653 2016-02-19

Publications (1)

Publication Number Publication Date
WO2017141538A1 true WO2017141538A1 (fr) 2017-08-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/087462 WO2017141538A1 (fr) 2016-02-19 2016-12-16 Joint fileté pour conduite de puits de pétrole

Country Status (15)

Country Link
US (1) US10900595B2 (fr)
EP (1) EP3418617B1 (fr)
JP (1) JP6187724B1 (fr)
CN (2) CN207131996U (fr)
AR (1) AR107648A1 (fr)
AU (1) AU2016393093B2 (fr)
BR (1) BR112018016593B1 (fr)
CA (1) CA3013300C (fr)
ES (1) ES2815848T3 (fr)
MX (1) MX2018009994A (fr)
MY (1) MY189310A (fr)
RU (1) RU2692177C1 (fr)
SA (1) SA518392131B1 (fr)
UA (1) UA120020C2 (fr)
WO (1) WO2017141538A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019082612A1 (fr) * 2017-10-25 2019-05-02 日本製鉄株式会社 Raccord fileté pour tuyau en acier
CN113107384A (zh) * 2021-04-20 2021-07-13 大庆市华禹石油机械制造有限公司 一种油管不粘扣连接结构及工艺

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2016393093B2 (en) * 2016-02-19 2019-05-02 Jfe Steel Corporation Threaded joint for oil well tubing
EP3260649B1 (fr) * 2016-06-21 2019-12-18 Energy Frontier Solutions S.L. Joint fileté pour tuyaux d'huile et de gaz
EA039155B1 (ru) * 2017-01-18 2021-12-10 Ниппон Стил Корпорейшн Резьбовое соединение для стальных труб
EA036471B1 (ru) * 2017-03-08 2020-11-13 Ниппон Стил Корпорейшн Резьбовое соединение для нефтяной скважины
CN112601908B (zh) * 2018-08-21 2022-10-21 日本制铁株式会社 钢管用螺纹接头
RU2757621C1 (ru) * 2018-10-02 2021-10-19 Ниппон Стил Корпорейшн Резьбовое соединение для стальных труб
WO2020137917A1 (fr) * 2018-12-25 2020-07-02 日本製鉄株式会社 Raccord fileté pour tuyau en acier
WO2021148951A1 (fr) * 2020-01-20 2021-07-29 United Drilling Tools Ltd. Raccord soudé à joint métallique pour gaine de conducteur

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006506582A (ja) * 2002-09-06 2006-02-23 テナリス・コネクシヨンズ・アクチエンゲゼルシヤフト ねじ管継手
JP4257707B2 (ja) 2002-04-30 2009-04-22 テナリス・コネクシヨンズ・アクチエンゲゼルシヤフト ネジ式管継手
WO2012002409A1 (fr) * 2010-06-30 2012-01-05 Ｊｆｅスチール株式会社 Couplage vissé de tuyau
WO2012056500A1 (fr) * 2010-10-29 2012-05-03 株式会社メタルワン Raccord à vis pour tube de puits de pétrole
WO2012118167A1 (fr) * 2011-02-28 2012-09-07 Ｊｆｅスチール株式会社 Raccord fileté pour tube
US20150316181A1 (en) * 2014-05-02 2015-11-05 Maximo Tejeda Threaded Connection

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1224745B (it) * 1988-10-03 1990-10-18 Dalmine Spa Giunto a tenuta ermetica metallica per tubi
UA82694C2 (uk) * 2003-06-06 2008-05-12 Sumitomo Metal Ind Нарізне з'єднання для сталевих труб
RU2310058C2 (ru) * 2005-09-15 2007-11-10 ОАО "Таганрогский металлургический завод" Герметичное резьбовое соединение нефтепромысловых труб
CN102187139B (zh) * 2008-10-20 2013-06-05 住友金属工业株式会社 钢管用螺纹接头
JP5725094B2 (ja) 2013-07-30 2015-05-27 Ｊｆｅスチール株式会社 耐久性に優れた油井管用ねじ継手
JP5971264B2 (ja) * 2014-01-10 2016-08-17 Ｊｆｅスチール株式会社 極厚肉油井管用ねじ継手
CN104895508B (zh) * 2015-06-29 2017-05-31 东营市永利精工石油机械制造有限公司 Hthp油气井用特殊螺纹接头
CN205012933U (zh) * 2015-09-18 2016-02-03 江苏常宝普莱森钢管有限公司 一种三台肩抗粘扣管体气密连接结构
RU160214U1 (ru) * 2015-10-20 2016-03-10 Общество с ограниченной ответственностью "Зеленодольский завод бурового оборудования" (ООО "ЗЗБО") Высокогерметичное упорное резьбовое соединение обсадных труб
AU2016393093B2 (en) * 2016-02-19 2019-05-02 Jfe Steel Corporation Threaded joint for oil well tubing

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4257707B2 (ja) 2002-04-30 2009-04-22 テナリス・コネクシヨンズ・アクチエンゲゼルシヤフト ネジ式管継手
JP2006506582A (ja) * 2002-09-06 2006-02-23 テナリス・コネクシヨンズ・アクチエンゲゼルシヤフト ねじ管継手
WO2012002409A1 (fr) * 2010-06-30 2012-01-05 Ｊｆｅスチール株式会社 Couplage vissé de tuyau
WO2012056500A1 (fr) * 2010-10-29 2012-05-03 株式会社メタルワン Raccord à vis pour tube de puits de pétrole
WO2012118167A1 (fr) * 2011-02-28 2012-09-07 Ｊｆｅスチール株式会社 Raccord fileté pour tube
US20150316181A1 (en) * 2014-05-02 2015-11-05 Maximo Tejeda Threaded Connection

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3418617A4

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019082612A1 (fr) * 2017-10-25 2019-05-02 日本製鉄株式会社 Raccord fileté pour tuyau en acier
JPWO2019082612A1 (ja) * 2017-10-25 2020-01-16 日本製鉄株式会社 鋼管用ねじ継手
EP3702656A4 (fr) * 2017-10-25 2020-10-28 Nippon Steel Corporation Raccord fileté pour tuyau en acier
AU2018354891B2 (en) * 2017-10-25 2021-05-06 Nippon Steel Corporation Threaded connection for steel pipe
EA038876B1 (ru) * 2017-10-25 2021-11-01 Ниппон Стил Корпорейшн Резьбовое соединение для стальной трубы
US11313181B2 (en) 2017-10-25 2022-04-26 Nippon Steel Corporation Threaded connection for steel pipe
CN113107384A (zh) * 2021-04-20 2021-07-13 大庆市华禹石油机械制造有限公司 一种油管不粘扣连接结构及工艺

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BR112018016593A2 (pt) 2018-12-18
ES2815848T3 (es) 2021-03-30
US10900595B2 (en) 2021-01-26
UA120020C2 (uk) 2019-09-10
AU2016393093B2 (en) 2019-05-02
EP3418617A4 (fr) 2019-03-20
CN207131996U (zh) 2018-03-23
AU2016393093A1 (en) 2018-08-02
MX2018009994A (es) 2018-11-09
US20190056049A1 (en) 2019-02-21
CN107101054B (zh) 2019-06-28
JP6187724B1 (ja) 2017-08-30
CA3013300C (fr) 2020-05-05
CA3013300A1 (fr) 2017-08-24
BR112018016593B1 (pt) 2021-10-26
EP3418617B1 (fr) 2020-08-05
EP3418617A1 (fr) 2018-12-26
AR107648A1 (es) 2018-05-16
MY189310A (en) 2022-02-03
JPWO2017141538A1 (ja) 2018-02-22
CN107101054A (zh) 2017-08-29
SA518392131B1 (ar) 2021-09-08
RU2692177C1 (ru) 2019-06-21

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